Fuel injection valve

ABSTRACT

A first spring axially urges a needle valve toward an injection hole. A second spring axially urges a movable core toward a stationary core with an urging force that is smaller than an urging force of the first spring. A stopper is placed on one axial side of the movable core where the injection hole is located. The stopper limits movement of the movable core toward the injection hole to limit an amount of compression of the second spring.

CROSS REFERENCE TO RELATED APPLICATION

This application is a continuation of U.S. application Ser. No.13/767,209, filed on Feb. 14, 2013 and is based on reference JapanesePatent Application No. 2012-33577 filed on Feb. 20, 2012 and JapanesePatent Application No. 2012-190113 filed on Aug. 30, 2012, each of whichare incorporated herein by reference.

TECHNICAL FIELD

The present disclosure relates to a fuel injection valve.

BACKGROUND

A solenoid type fuel injection valve (injector) is known. The solenoidtype fuel injection valve receives high pressure fuel from a deliverypipe, which accumulates fuel received from a high pressure pump thatpumps fuel from a fuel tank. The fuel injection valve injects thereceived high pressure fuel into an internal combustion engine of avehicle (e.g., an automobile).

For instance, JP2002-506502A (corresponding to U.S. Pat. No.6,279,873B1) teaches such a fuel injection valve. Specifically, in adeenergized state of a coil of this fuel injection valve, a needle valveis urged by an urging force of a first return spring, so that the needlevalve is seated against a valve seat. Furthermore, a movable core isurged against a stopper element by an urging force of a second returnspring. At this time, a small gap is formed between a flange of theneedle valve and the movable core.

At the time of executing a valve-opening operation, the coil isenergized, so that the movable core is magnetically attracted to thestationary core, and the movable core abuts against the flange of theneedle valve in the accelerated state of the movable core. In this way,a valve-opening time period, which is a time period required to open theinjection hole by lifting the needle valve away from the valve seat, isshortened.

However, in the fuel injection valve of JP2002-506502A (corresponding toU.S. Pat. No. 6,279,873B1), both of the first return spring and thesecond return spring urge the movable core toward the fuel injectionhole at the time of executing a valve-closing operation, which isexecuted to seat the needle valve against the valve seat. Therefore,when the state of the coil is changed from the energized state to thedeenergized state, the movable core, which is moved together with theneedle valve toward the injection hole, is urged by the urging force ofthe second return spring and the inertia of the movable core and therebycollides against the stopper element upon the seating of the needlevalve against the valve seat. Thereafter, the movable core rebounds fromthe stopper element. When the collision force of the movable coreagainst the flange of the needle is increased, a secondary valve-openingmovement of the needle valve occurs to reopen the injection hole.Thereby, it may possibly be difficult to accurately control the fuelinjection quantity of the fuel injection valve.

Furthermore, when the collision force of the movable core against thestopper element is increased, the collision noise may possibly beincreased. Also, the collision of the movable core against the stopperelement may possibly damage the movable core and/or the stopper element.

SUMMARY

The present disclosure addresses the above disadvantage. According tothe present disclosure, there is provided a fuel injection valve, whichincludes a housing, a needle valve, a coil, a stationary core, a movablecore, a first spring, a second spring and a stopper. The housing isconfigured into a tubular body and has an injection hole, a fuel passageand a valve seat. Fuel is injected through the injection hole. The fuelpassage is communicated with the injection hole. The valve seat isformed in an inner wall of the fuel passage. The needle valve isreceived in the housing and is axially reciprocatable in the housing.The needle valve has a flange that radially outwardly projects. Theneedle valve opens the injection hole when the needle valve is liftedaway from the valve seat. The needle valve closes the injection holewhen the needle valve is seated against the valve seat. The coilgenerates a magnetic field in an energized state of the coil. Thestationary core is fixed in the housing at a corresponding location thatis within a range of the magnetic field generated from the coil. Themovable core is axially reciprocatable and is placed on one axial sideof the stationary core where the injection hole is located. The movablecore is contactable with an end surface of the flange of the needlevalve, which is located on an axial side where the injection hole islocated. The first spring axially urges the needle valve toward theinjection hole. The second spring axially urges the movable core towardthe stationary core with an urging force that is smaller than an urgingforce of the first spring, which axially urges the needle valve towardthe injection hole. The stopper is placed on one axial side of themovable core where the injection hole is located. The stopper limitsmovement of the movable core toward the injection hole to limit anamount of compression of the second spring.

BRIEF DESCRIPTION OF THE DRAWINGS

The drawings described herein are for illustration purposes only and arenot intended to limit the scope of the present disclosure in any way.

FIG. 1 is a cross-sectional view of a fuel injection valve according toa first embodiment of the present disclosure;

FIG. 2 is a partial enlarged cross-sectional view of FIG. 1 showing amain feature of the fuel injection valve of the first embodiment;

FIG. 3 is a cross-sectional view taken along line in FIG. 2;

FIG. 4 is a partial enlarged view of the fuel injection valve of thefirst embodiment, showing a valve-opening operation of the fuelinjection valve;

FIG. 5 is a partial enlarged view of the fuel injection valve of thefirst embodiment, showing a valve-closing operation of the fuelinjection valve;

FIG. 6 is a diagram showing a flow of a magnetic flux in thevalve-opening operation of the fuel injection valve of the firstembodiment;

FIG. 7 is a partial enlarged cross-sectional view showing a main featureof a fuel injection valve according to a second embodiment of thepresent disclosure;

FIG. 8 is a partial enlarged cross-sectional view showing a main featureof a fuel injection valve according to a third embodiment of the presentdisclosure;

FIG. 9 is a partial enlarged cross-sectional view showing a main featureof a fuel injection valve according to a fourth embodiment of thepresent disclosure; and

FIG. 10 is a partial enlarged cross-sectional view showing the mainfeature of the fuel injection valve according to the fourth embodiment.

DETAILED DESCRIPTION

Embodiments of the present disclosure will be described with referenceto the accompanying drawings.

First Embodiment

FIGS. 1 to 6 show a fuel injection valve according to a first embodimentof the present disclosure. The fuel injection valve 1 receives highpressure fuel from a delivery pipe, which accumulates fuel received froma high pressure pump that pumps fuel from a fuel tank. The fuelinjection valve 1 injects the received high pressure fuel into aninternal combustion engine of a vehicle (e.g., an automobile).

As shown in FIGS. 1 and 2, the fuel injection valve 1 includes a housing10, a needle valve 30, a coil 40, a stationary core 50, a movable core60 and a stopper 80.

The housing 10 includes a tubular member 11, a non-magnetic portion 12,a holder 13, an inlet member 15 and a nozzle body 20. The housing 10serves as a housing of the present disclosure.

The tubular member 11, the non-magnetic portion 12 and the holder 13 areconfigured into generally cylindrical tubular bodies, respectively, andare joined one after another in this order from a fuel inlet 14 side(i.e., an axial side where the fuel inlet 14 is located). The tubularmember 11 and the holder 13 are made of a magnetic material. Thenon-magnetic portion 12 is made of a non-magnetic material and limitsmagnetic short-circuit between the tubular member 11 and the holder 13.The inlet member 15, which is configured into a tubular body and formsthe fuel inlet 14, is joined to an end portion of the tubular member 11,which is opposite from the non-magnetic portion 12. A filter 16 isplaced in the inlet member 15 at a location that is radially inward ofthe inlet member 15. The fuel, which is supplied through the fuel inlet14, is filtered through the filter 16 and is supplied to an upstreampassage 17 that is formed in an inside of the housing 10.

The housing 10 has a nozzle body 20 at an end portion of the housing 10,which is opposite from the non-magnetic portion 12 of the holder 13. Thenozzle body 20 is configured into a cup shape body and has a bottomportion (a bottom wall portion) 21 and a tubular portion (peripheralwall portion) 22. The tubular portion 22 is joined to an innerperipheral portion of the holder 13. An injection hole 23 is formed toaxially extend through the bottom portion 21.

A valve seat 24, which is recessed and is tapered, is formed in an innerwall of the bottom portion 21.

The needle valve 30 is configured into a cylindrical rod body and isreceived in the housing 10 such that the needle valve 30 isreciprocatable in the axial direction in the housing 10.

The needle valve 30 has a flange 31. The flange 31 radially outwardlyprojects from a fuel inlet 14 side end portion of the needle valve 30(i.e., an end portion of the needle valve 30 located on an axial sidewhere the fuel inlet 14 is placed). The flange 31 is configured into anannular form. The flange 31 can contact a fuel inlet 14 side end surfaceof the movable core 60 (i.e., an end surface of the movable core 60located on an axial side where the fuel inlet 14 is placed).

A downstream passage 19 is radially defined between the needle valve 30and the holder 13 and extends in the axial direction in the inside ofthe holder 13. The upstream passage 17 and the downstream passage 19serve as a fuel passage of the present disclosure.

The needle valve 30 has an inside passage 36, which axially extendsalong a central axis of the needle valve 30. The needle valve 30 has aflow outlet 32, which radially extends through the needle valve 30 froman inner wall of the inside passage 36 to an outer wall of the needlevalve 30. Thereby, the inside passage 36 communicates between theupstream passage 17 and the downstream passage 19 through the flowoutlet 32.

A seat portion 33 is formed in an injection hole 23 side end portion ofthe needle valve 30 (i.e., an end portion of the needle valve 30 locatedon an axial side where the injection hole 23 is placed). The seatportion 33 is contactable with, i.e., is seatable against the valve seat24. A slidable portion 34 is formed in the needle valve 30 at alocation, which is axially spaced from the seat portion 33 by apredetermined distance. The slidable portion 34 is slidable along aninner peripheral wall of the tubular portion 22 of the nozzle body 20. Achamfered portion 35 is formed in a portion of an outer peripheral wallof the slidable portion 34. Fuel can flow between the chamfered portion35 and the inner peripheral wall of the tubular portion 22.

When the seat portion 33 is seated against the valve seat 24, the needlevalve 30 closes the downstream passage 19, which is communicated withthe injection hole 23. Then, when the seat portion 33 is lifted awayfrom the valve seat 24, the needle valve 30 opens the downstream passage19, which is communicated with the injection hole 23.

Hereinafter, the lifting direction of the needle valve 30 away from thevalve seat 24 will be referred to as a valve-opening direction.Furthermore, a seating direction of the needle valve 30 toward the valveseat 24 will be referred to as a valve-closing direction.

The fuel injection valve 1 includes a solenoid drive device, whichdrives the needle valve 30. The solenoid drive device includes a coil40, a stationary core 50 and a movable core 60.

A spool 41 is placed on a radially outer side of the tubular member 11and the non-magnetic portion 12 of the housing 10. The coil 40 is woundaround the spool 41. A yoke 42, which is configured into a tubular bodyand is made of a magnetic material, covers an outer peripheral portionof the coil 40. The coil 40 is electrically connected to terminals 44 ofa connector 43. When the coil 40 is energized through the connector 43,the coil 40 generates a magnetic field.

The stationary core 50 is configured into a generally cylindricaltubular body and is made of a magnetic material. The stationary core 50is fixed to an inner peripheral wall of the tubular member 11 and aninner peripheral wall of the non-magnetic portion 12. A hole 51 isformed in the stationary core 50 such that the hole 51 axially extendsalong a central axis of the stationary core 50. A first spring 70 isinserted in the hole 51 of the stationary core 50. One end portion ofthe first spring 70 contacts the flange 31 of the needle valve 30, andthe other end portion of the first spring 70, which is opposite from theone end portion of the first spring 70, contacts an adjusting pipe 71that is securely press-fitted into an inside of the stationary core 50.A load of the first spring 70 is set depending on the amount ofinsertion of the adjusting pipe 71 into the inside of the stationarycore 50. The first spring 70 urges the needle valve 30 toward theinjection hole 23.

The movable core 60 is configured into a generally cylindrical tubularbody and is made of a magnetic material. The movable core 60 is formedseparately from the needle valve 30 and is axially placed on theinjection hole 23 side of the stationary core 50.

The movable core 60 is placed radially inward of the housing 10 in amanner that enables axial reciprocation of the movable core 60 in thehousing 10. In a deenergized state of the coil 40, a predetermined gap90 is formed between the movable core 60 and the stationary core 50.

A center hole 61 is formed in the movable core 60 such that the centerhole 61 axially extends through the movable core 60 at a center portionof the movable core 60. The needle valve 30 is received through thecenter hole 61 of the movable core 60. A portion of the needle valve 30,which is placed radially inward of the movable core 60, is slidablealong an inner peripheral wall of the center hole 61 of the movable core60. The needle valve 30 is reciprocatably received in the housing 10such that the needle valve 30 is guided at two portions of the needlevalve 30, i.e., the slidable portion 34 of the needle valve 30, which isaxially located at the nozzle body 20 side, and the portion of theneedle valve 30, which is located radially inward of the movable core60.

The movable core 60 includes a plurality of communication holes 62. Thecommunication holes 62 communicate between the gap 90, which is formedbetween the stationary core 50 and the movable core 60, and a gap 91,which is formed between the movable core 60 and the stopper 80. Theaxial moving speed of the movable core 60 is adjustable through settingof the number of the communication holes 62, the inner diameter(s) ofthe communication holes 62 and the location(s) of the communicationholes 62. In the present embodiment, the number of the communicationholes 62 is three, and these communication holes 62 are arranged oneafter another in the circumferential direction.

A second spring 72 is placed such that one end portion of the secondspring 72 contacts an end surface of a recess 67 of the movable core 60,which is axially placed on the injection hole 23 side, and the other endportion of the second spring 72 contacts a stepped surface 73 of theholder 13. The second spring 72 urges the movable core 60 in thevalve-opening direction. In the deenergized state of the coil 40, thesecond spring 72 exerts the urging force against the movable core 60, sothat the fuel inlet 14 side end surface of the movable core 60 contactsthe injection hole 23 side end surface of the flange 31 of the needlevalve 30. Therefore, when the coil 40 is energized, the movable core 60and the needle valve 30 are simultaneously moved together. Thus, thevalve-opening response of the fuel injection valve 1 at the time oflifting the needle valve 30 away from the valve seat 24 is improved.

The urging force of the first spring 70 is set to be higher than theurging force of the second spring 72. Therefore, in the deenergizedstate of the coil 40, the seat portion 33 of the needle valve 30 isseated against the valve seat 24.

The stopper 80 is provided on the injection hole 23 side of the movablecore 60. The stopper 80 is made of a non-magnetic material and includesa circular disk portion (a ring portion, an annular portion) 81 and atubular portion 82. The tubular portion 82 axially extends from an innerperipheral edge part of the circular disk portion 81 toward theinjection hole 23. An outer peripheral wall of the tubular portion 82 ispress-fitted to an inner peripheral wall of the holder 13.Alternatively, the stopper 80 may be configured such that the circulardisk portion 81 is press-fitted to the inner peripheral wall of theholder 13.

The circular disk portion 81 of the stopper 80 limits movement of themovable core 60 toward the injection hole 23 side to limit the amount ofcompression of the second spring 72 at the time of moving the movablecore 60 toward the injection hole 23. In FIG. 3, the movable core 60 isindicated by a dotted line. As shown in FIGS. 2 and 3, a radial length(radial extent) L1 of a first contact surface 83 of the circular diskportion 81, which is located on the movable core 60 side, is larger thana radial length (radial extent) L2 of a second contact surface 66 of themovable core 60, which is located on the injection hole 23 side. Thatis, when the first contact surface 83 and the second contact surface 66are projected onto an imaginary surface (imaginary plane) that isperpendicular to the axis of the needle valve 30, the second contactsurface 66 is entirely received within the inside of the first contactsurface 83. With this construction, a squeezing force, which is exertedat the time of colliding the second contact surface 66 against the firstcontact surface 83, and a linking force, which is exerted at the time ofseparating the second contact surface 66 away from the first contactsurface 83, are increased. The squeezing force is a force of the fluidheld between the first contact surface 83 and the second contact surface66. The linking force is a force, which interferes with separationbetween two articles in the fluid.

As shown in FIG. 2, an inner diameter D1 of the tubular portion 82 ofthe stopper 80 is set to be slightly larger than an outer diameter D2 ofthe second spring 72 to limit tilting of the second spring 72. With thissetting, the inner peripheral wall of the tubular portion 82 of thestopper 80 can axially guide the second spring 72. Thus, a predeterminedorientation of the second spring 72 is maintained, and thereby the loadof the second spring 72, which urges the movable core 60, is stabilized.Furthermore, a predetermined orientation of the movable core 60 ismaintained, and thereby generation of an unintentional frictional forcebetween the movable core 60 and the holder 13 or the non-magneticportion 12 can be limited.

Next, the operation of the fuel injection valve 1 will be described.

The fuel, which is supplied from the fuel inlet 14 to the upstreampassage 17, is filled in the inside passage 36 of the needle valve 30and the downstream passage 19.

FIG. 2 shows the deenergized state of the coil 40. The needle valve 30is urged by the first spring 70, so that the seat portion 33 is seatedagainst the valve seat 24. The movable core 60 is urged against theinjection hole 23 side end surface of the flange 31 of the needle valve30 by the urging force of the second spring 72. At this time, the smallgap 91 is formed between the movable core 60 and the stopper 80. The gap91 between the movable core 60 and the stopper 80 is exaggerated inFIGS. 2 and 4. Actually, the axial size of the gap 91 is, for example,about 30 μm.

Now, a valve-opening operation of the fuel injection valve 1 will bedescribed.

When the coil 40 is energized, the magnetic field is generated by thecoil 40. Therefore, as indicated by arrows B in FIG. 6, the magneticflux flows through a magnetic circuit, which is formed by the stationarycore 50, the tubular member 11, the yoke 42, the holder 13 and themovable core 60. The stopper 80 is made of the non-magnetic material.Therefore, the leakage of the magnetic flux from the holder 13 to thestopper 80 is reduced or limited. Thus, the density of the magneticflux, which flows between the movable core 60 and the stationary core50, is increased.

When the magnetic attractive force is exerted between the movable core60 and the stationary core 50, the movable core 60 is magneticallyattracted to the stationary core 50, as indicated in FIG. 4. When themovable core 60 contacts the stationary core 50, the communication holes62 of the movable core 60 are closed by the stationary core 50.Furthermore, the movable core 60 contacts the flange 31, so that theneedle valve 30 and the movable core 60 are moved together in thevalve-opening direction. As a result, the seat portion 33 is lifted awayfrom the valve seat 24 to open the injection hole 23, and thereby thefuel is injected through the injection hole 23.

Next, a valve-closing operation of the fuel injection valve 1 will bedescribed.

When the coil 40 is deenergized, the needle valve 30 is moved togetherwith the movable core 60 in the valve-closing direction. As shown inFIG. 2, when the seat portion 33 of the needle valve 30 is seatedagainst the valve seat 24, the fuel injection is stopped.

Thereafter, the movable core 60 is kept moving in the valve-closingdirection by inertia. At this time, the urging force of the secondspring 72 is exerted to reduce the moving speed of the movable core 60.As shown in FIG. 5, when the movable core 60 contacts the stopper 80,the movement of the movable core 60 in the valve-closing direction islimited. Therefore, the amount of compression of the second spring 72 islimited.

When the movable core 60 contacts the stopper 80, the communicationholes 62 of the movable core 60 are closed by the stopper 80. The firstcontact surface 83 of the stopper 80 can entirely contact the secondcontact surface 66 of the movable core 60. Therefore, the contactpressure, which is exerted between the first contact surface 83 and thesecond contact surface 66 at the time of collision of the second contactsurface 66 against the first contact surface 83, is relatively small.Furthermore, the squeezing force, which is exerted at the time ofcolliding the second contact surface 66 against the first contactsurface 83, and the linking force, which is exerted at the time ofseparating the second contact surface 66 away from the first contactsurface 83, are relatively large. Thereby, the damper effect, whichreduces the moving speed of the movable core 60, is generated. Thus,when the movable core 60 rebounds from the stopper 80 after thecollision of the movable core 60 against the stopper 80, the movingspeed of the movable core 60 in the rebound motion of the movable core60 away from the stopper 80 is reduced.

Furthermore, the axial size of the gap 91 between the movable core 60and the stopper 80 is set to a value, which enables reduction of thecollision force of the movable core 60 against the flange 31 of theneedle valve 30 at the time of rebound of the movable core 60 toward thestationary core 50 to limit the secondary valve-opening movement of theneedle valve 30 away from the valve seat 24.

Specifically, the resilient force, which is accumulated in the secondspring 72, is reduced by the stopper 80, so that the moving speed of themovable core 60 in the rebound motion of the movable core 60 toward thestationary core 50 is reduced. Furthermore, the gap 91 between themovable core 60 and the stopper 80 is appropriately set, so that thecollision force of the movable core 60 against the flange 31 of theneedle valve 30 is reduced. Therefore, as shown in FIG. 2, when themovable core 60 contacts the flange 31 of the needle valve 30, themovement of the needle valve 30 in the valve-opening direction islimited. Thus, the secondary valve-opening movement of the needle valve30 away from the valve seat 24 is advantageously limited.

Now, the advantages of the present embodiment will be described.

(1) In the present embodiment, when the energization of the coil 40 isturned off to place the coil 40 into the deenergized state in thevalve-closing operation of the needle valve 30, the movable core 60 ismoved together with the needle valve 30 toward the injection hole 23 bythe urging force of the first spring 70. At this time, the movement ofthe movable core 60 toward the injection hole 23 is limited by thestopper 80, so that the movement of the movable core 60 toward theinjection hole 23 is minimized. Therefore, the amount of compression ofthe second spring 72 is reduced, and thereby the urging force, which isaccumulated in the second spring 72, is reduced.

Furthermore, the contact pressure, which is exerted between the firstcontact surface 83 of the stopper 80 and the second contact surface 66of the movable core 60 at the time of collision of the second contactsurface 66 of the movable core 60 against the first contact surface 83of the stopper 80, is relatively small. Furthermore, the squeezingforce, which is exerted between the first contact surface 83 and thesecond contact surface 66 at the time of collision of the second contactsurface 66 against the first contact surface 83, and the linking force,which is exerted between the first contact surface 83 and the secondcontact surface 66 at the time of separation of the first contactsurface 83 and the second contact surface 66 from each other, arerelatively large. Therefore, the damping effect, which reduces themoving speed of the movable core 60, can be generated. Thus, the movingspeed of the movable core 60 in the rebound motion of the movable core60 away from the stopper 80 is reduced, and thereby the collision forceof the movable core 60 against the needle valve 30 is reduced.

Furthermore, the axial size of the gap 91, which is formed between thestopper 80 and the movable core 60 in the deenergized state of the coil40, is set to the value, which enables limiting of the secondary valveopening movement of the needle valve 30 away from the valve seat 24 byreducing the collision force of the movable core 60 against the flange31 of the needle valve 30 at the time of the rebound of the movable core60 toward the stationary core 50.

Therefore, the fuel injection valve 1 can limit the secondary opening ofthe injection hole 23, which results from the secondary valve-openingmovement of the needle valve 30 away from the valve seat 24, at the timeof valve-closing operation of the needle valve 30.

Furthermore, the contact pressure, which is exerted between the firstcontact surface 83 and the second contact surface 66 at the time ofcollision of the second contact surface 66 against the first contactsurface 83, is reduced. Therefore, the durability of the stopper 80 andthe durability of the movable core 60 can be improved.

(2) In the present embodiment, the movable core 60 has the communicationholes 62. The communication holes 62 communicate between the gap 90,which is formed between the stationary core 50 and the movable core 60,and the gap 91, which is formed between the movable core 60 and thestopper 80. The axial moving speed of the movable core 60 in thereciprocating motion thereof is adjustable through setting of thelocation(s), the inner diameter(s) and the number of the communicationholes 62. Therefore, the fuel injection valve 1 can limit the secondaryvalve-opening movement of the needle valve 30 away from the valve seat24 at the time of valve-closing operation of the needle valve 30 and canimprove the valve-opening response and the valve-closing response of theneedle valve 30 at the time of energization and deenergization,respectively, of the coil 40.

(3) In the present embodiment, the tubular portion 82 of the stopper 80can axially guide the second spring 72 along the inner peripheral wallof the tubular portion 82 of the stopper 80. Thereby, the predeterminedorientation of the second spring 72 is maintained. Thus, the load of thesecond spring 72 against the movable core 60 is stabilized, and thepredetermined orientation of the movable core 60 is maintained. As aresult, the generation of the unintentional frictional force between themovable core 60 and the inner peripheral wall of the housing can belimited, and thereby the smooth movement of the movable core 60 ismaintained. Therefore, the fuel injection valve 1 can limit thesecondary valve-opening movement of the needle valve 30 away from thevalve seat 24 at the time of valve-closing operation of the needle valve30 and can improve the valve-opening response and the valve-closingresponse of the needle valve 30 at the time of energization anddeenergization, respectively, of the coil 40.

(4) In the present embodiment, the inside passage 36 of the needle valve30 communicates between the upstream passage 17 and the downstreampassage 19 through the flow outlet 32, which is formed at the radiallyinner side of the stopper 80. In this way, even when the communicationholes 62 of the movable core 60 are closed by the stationary core 50 orthe stopper 80, the fuel can flow between the upstream passage 17 andthe downstream passage 19 through the inside passage 36 of the needlevalve 30.

(5) In the present embodiment, the stopper 80 is made of thenon-magnetic material, so that the magnetic resistance of the stopper 80is relatively large. Thus, the leakage of the magnetic flux to thestopper 80 can be limited at the time of energization of the coil 40, sothat the density of the magnetic flux between the movable core 60 andthe stationary core 50 is increased. In this way, it is possible toimprove the valve-opening response of the fuel injection valve 1.

(6) In the present embodiment, the needle valve 30 and the movable core60 are formed separately. Therefore, the collision force, which isexerted at the time of seating of the needle valve 30 against the valveseat 24, is relatively small. Thus, the bounce, i.e., rebound of theneedle valve 30 from the valve seat 24 is limited to limit the secondaryinjection of fuel through the injection hole 23. Furthermore, theoperational noise is reduced at the time of seating the needle valve 30against the valve seat 24.

Second Embodiment

FIG. 7 shows a fuel injection valve according to a second embodiment ofthe present disclosure. In the following embodiments, the components,which are similar to those of the first embodiment, will be indicated bythe same reference numerals and will not be described again to avoidredundancy.

In the second embodiment, a stopper 84 is made only of a circular diskportion. That is, the stopper 84 is configured into the circular diskbody (a ring body, i.e., an annular body). The outer peripheral wall ofthe stopper 84 is press-fitted to the inner peripheral wall of theholder 13. Furthermore, the inner diameter D3 of the stopper 84 islarger than the outer diameter D2 of the second spring 72 to such adegree that the second spring 72 does not contact the stopper 84 upontilting of the second spring 72.

In the second embodiment, the structure of the stopper 84 is simplified,and thereby the stopper 84 can be easily manufactured. Thereby, themanufacturing costs can be reduced.

Furthermore, the contact between the second spring 72 and the stopper 84is limited. Therefore, the generation of the unintentional frictionalforce between the second spring 72 and the stopper 84 can be limited.

Third Embodiment

FIG. 8 shows a fuel injection valve according to a third embodiment ofthe present disclosure. In the third embodiment, the stopper 85 and theholder 13 are formed integrally and seamlessly.

In the third embodiment, the stopper 85 can be manufactured only throughmanagement of a distance H between the stepped surface 73 of the holder13 and the moveable core 60 side end surface of the stopper 85. Thus,the number of points of the components, at which the size needs to bemanaged, can be reduced. Therefore, the clearance between the movablecore 60 and the stopper 85 can be accurately formed.

Fourth Embodiment

FIGS. 9 and 10 show a fuel injection valve according to a fourthembodiment of the present disclosure.

Although it is difficult to see the gap 91 between the movable core 60and the stopper 86 in FIG. 10, the axial size of the gap 91 is set to beabout 30 μm in the deenergized state of the coil 40 like in the first tothird embodiments. Furthermore, in FIG. 10, the coil, the yoke and thespool are omitted for the sake of simplicity.

In the fourth embodiment, a stopper 86 is configured into a ring body(annular body). Specifically, an inner diameter D4 of the stopper 86 ofthe fourth embodiment is larger than the inner diameter D3 of thestopper 84 of the second embodiment. Therefore, the space, which islocated radially inward of the stopper 86, is widened, and the pressureloss of the fuel, which flows through the downstream passage 19, isreduced.

An outer peripheral wall of the stopper 86 is securely press-fitted tothe inner peripheral wall of the holder 13. Furthermore, the injectionhole 23 side end surface of the stopper 86 contacts the stepped surface131 of the holder 13.

In the present embodiment, the number of the communication holes 62,which are arranged one after another in the circumferential direction inthe movable core 60, is four. Here, it should be noted that, forinstance, the number of the communication holes 62 and the innerdiameter(s) of the communication holes 62 can be freely set depending ona need. One end portion of each communication hole 62 is communicatedwith the gap 90, which is formed between the movable core 60 and thestationary core 50, and the other end portion of the communication hole62 is communicated with the downstream passage 19. In the contact stateof the movable core 60, in which the movable core 60 contacts thestopper 86, about one half of the opening of the communication hole 62opens to the downstream passage 19.

In the fourth embodiment, the stopper 86 is formed as the simple ringbody, so that the processing and the size management of the stopper 86are relatively easy. Furthermore, since the profile of the stopper 86 isreduced, the manufacturing costs can be reduced, and the weight of thefuel injection valve 1 can be reduced.

Furthermore, the pressure loss of fuel, which flows through thedownstream passage 19, can be reduced by increasing the inner diameterof the stopper 86 and increasing the inside space of the stopper 86.

Even in the fourth embodiment, the stopper 86 limits the movement of themovable core 60 at the time of the valve-closing operation of the needlevalve 30 to limit the amount of compression of the second spring 72.That is, when the movable core 60 contacts the stopper 86, the resilientforce, which is accumulated in the second spring 72, is reduced.

Furthermore, the axial size of the gap 91 between the movable core 60and the stopper 86 is set to the value, which enables the reduction ofthe collision force of the movable core 60 against the flange 31 of theneedle valve 30 at the time of rebound of the movable core 60 toward thestationary core 50 to limit the secondary valve-opening movement of theneedle valve 30 away from the valve seat 24.

Therefore, the fuel injection valve 1 can limit the secondary opening ofthe injection hole 23 by limiting the secondary valve-opening movementof the needle valve 30 away from the valve seat 24 at the time ofvalve-closing operation of the needle valve 30.

Now, a modification of the above embodiments will be described.

In the above embodiments, the fuel injection valve, which injects thefuel into the internal combustion engine (more specifically, a cylinderof the internal combustion engine), is described. In a modification ofthe above embodiment(s), the fuel injection valve may be configured toinject fuel into, for example, an intake air passage of the internalcombustion engine.

The present disclosure is not limited the above embodiments andmodification thereof. That is, the above embodiments and modificationthereof may be modified in various other ways without departing from theprinciple of the present disclosure.

What is claimed is:
 1. A fuel injection valve comprising: a housing thathas: an injection hole, through which fuel is injected; a fuel passagethat is communicated with the injection hole; and a valve seat that isformed in an inner wall of the fuel passage; a valve that is axiallyreciprocatable, wherein: the valve has a flange that radially outwardlyprojects; the valve opens the injection hole when the valve is liftedaway from the valve seat; and the valve closes the injection hole whenthe valve is seated against the valve seat; a coil that generates amagnetic field in an energized state of the coil; a stationary core; amovable core that is axially reciprocatable and is placed on one axialside of the stationary core where the injection hole is located, whereinthe movable core is engageable with the valve; a first spring thataxially urges the valve toward the injection hole; a second spring thataxially urges the movable core toward the stationary core with an urgingforce that is smaller than an urging force of the first spring, whichaxially urges the valve toward the injection hole; and a stopper that isplaced on one axial side of the movable core where the injection hole islocated, wherein: the stopper limits movement of the movable core towardthe injection hole to limit an amount of compression of the secondspring; the stopper is directly abuttable with the movable core; a gapis present between the movable core and the stopper when the coil is ina deenergized state.
 2. The fuel injection valve according to claim 1,wherein an axial size of the gap, which is formed between the stopperand the movable core in the deenergized state of the coil, is set to avalue, which enables limiting of secondary valve opening movement of thevalve away from the valve seat caused by abutment of the movable coreagainst the flange of the valve, which is in turn caused by rebound ofthe movable core from the stopper after contacting of the movable coreagainst the stopper due to inertial movement of the movable coretogether with the valve toward the injection hole upon changing of astate of the coil from the energized state to the deenergized state ofthe of the coil.
 3. The fuel injection valve according to claim 1,wherein the movable core has at least one communication hole thatcommunicates between a gap, which is formed between the movable core andthe stationary core in a deenergized state of the coil, and a downstreampassage, which is formed between an inner peripheral wall of the stopperand the valve.
 4. The fuel injection valve according to claim 1, whereinthe stopper is configured into a ring body and is fixed to an inner wallof the housing.
 5. The fuel injection valve according to claim 1,wherein: the stopper includes: a circular disk portion that iscontactable with the movable core; and a tubular portion that axiallyextends from an inner peripheral edge part of the circular disk portiontoward the injection hole; and the tubular portion of the stopper isconfigured to axially guide the second spring along an inner peripheralwall of the tubular portion.
 6. The fuel injection valve according toclaim 1, wherein: the stopper includes only a circular disk portion thatis contactable with the movable core; and an inner diameter of thecircular disk portion is set to a value that is larger than an outerdiameter of the second spring and limits contact of the second springagainst the circular disk portion upon tilting of the second spring. 7.The fuel injection valve according to claim 1, wherein the stopper isformed separately from the housing and is made of a non-magneticmaterial.
 8. The fuel injection valve according to claim 1, wherein thestopper is formed integrally with the housing.
 9. The fuel injectionvalve according to claim 5, wherein: the at least one communication holeof the movable core is closed by the stationary core when the movablecore contacts the stationary core; and the at least one communicationhole of the movable core is closed by the stopper when the movable corecontacts the stopper.
 10. The fuel injection valve according to claim 1,wherein the valve has: an inside passage that axially extends along acentral axis of the valve; and a flow outlet that radially extends froman inner wall of the inside passage to an outer wall of the valve. 11.The fuel injection valve according to claim 1, wherein the gap, which isformed between the stopper and the movable core in the deenergized stateof the coil, is an uninterrupted axial gap, which radially extends froma radially inner peripheral edge of an end surface of the movable coreto a radially outer peripheral edge of the end surface of the movablecore.
 12. The fuel injection valve according to claim 1, wherein themovable core is entirely lifted away from the stopper and is entirelyseparated from the stopper by the gap, which is formed between thestopper and the movable core, in the deenergized state of the coil. 13.The fuel injection valve according to claim 1, wherein the stopper isradially entirely spaced from and is thereby entirely separated from thevalve.